JP2010144743A - Continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission which allows the elimination of the need for carrying reaction to a traction force in a power roller by a rotational driving means. <P>SOLUTION: For instance, a traction force F1 produced in a power roller 14 during running is decomposed into forces F2, F3 in the inner and outer peripheral sides of a planet gear 33 to be transmitted to a ring gear 26A as a force F5 in a rotating direction and to a sun gear 25A as a force F6 in a rotating direction. The forces F5, F6 are transmitted to the inner and outer peripheries of a control pinion 27 as forces F7, F8. A force F9 equivalent to the traction force F1 is transmitted with respect to a pinion shaft 28e keeping the center on almost the same diameter as the center of a power roller 14. By fixing a carrier for supporting the control pinion 27 to a transmission case, the whole of the traction force F1 is carried by the case. As a result, the need for outputting reaction by a motor unit 29 is eliminated. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a continuously variable transmission mounted on a vehicle such as an automobile or a working vehicle, and more specifically, by controlling a planet gear supporting a power roller by rotational driving of a sun gear and a ring gear, The present invention relates to a toroidal continuously variable transmission that controls a change in a typical gear ratio.

  In recent years, full-toroidal continuously variable transmissions have been proposed as continuously variable transmissions mounted on vehicles such as automobiles and work vehicles (see Patent Document 1). This is composed of an input disk, an output disk, and a power roller sandwiched between the two disks, and a gear ratio is obtained by a contact position (contact radius) with both disks based on the inclination of the power roller. In this toroidal continuously variable transmission, the tilt angle of the power roller changes autonomously by controlling the movement of the rotation center of the power roller with respect to the surface direction of both disks by a link mechanism connected to a hydraulic servo. As a result, the gear ratio is changed.

  The toroidal continuously variable transmission of Patent Document 1 will be briefly described with reference to FIGS. As shown in FIGS. 5A and 5B, the toroidal-type continuously variable transmission device includes an input disk 111, an output disk 112, and a power roller 113 sandwiched between the disks 111 and 112. The power roller 113 is supported by a carriage 116 so as to be rotatable about an axis P. The carriage 116 is connected to a piston of a hydraulic servo 115 at one end thereof. The power roller 113 rotates about the axis P in the ω1 direction based on the rotation of the input disk 111, and the output disk 112 is rotated in the ω3 direction based on this rotation. At this time, the traction force F11 is applied to the power roller 113 when torque is transmitted from the input disk 111, and the traction force F12 as a reaction force is applied when torque is transmitted from the power roller 113 to the output disk 112. Works. The traction forces F11 and F12 acting on the power roller 113 are balanced with the reaction force F13 acting on the carriage 116 by the pressing drive of the hydraulic servo 115.

  For example, when the reaction force F13 is weakened by the control of the hydraulic servo 115, the balance of force is lost and the position of the power roller 113 moves toward the hydraulic servo 115 as shown in FIGS. 6 (a) and 6 (b). 6B, the speed vector V′r of the power roller 113 does not change at the contact portion 117 between the output disk 112 and the power roller 113, but the speed vector V′d of the output disk 112 does not change. Therefore, the speed vector V′d of the output disk 112 and the speed vector V′r of the power roller 113 are not parallel to each other because the tangential direction of the contact portion 117 is obtained. Further, in the contact portion 117, a traction force F14 in the same direction as the difference between the velocity vector V′d and the velocity vector V′r is generated, and the traction force F14 acts on the power roller 113.

  On the other hand, a similar action occurs between the power roller 113 and the input disk 111, and a force opposite to the traction force F14 acts on the power roller 113. 7A and 7B, the shaft P of the power roller 113 is tilted by the action of the traction force and the traction force F14 generated between the power roller 113 and the input disk 111, that is, the input disk. The speed ratio (contact radius) of the output disk 112 with respect to 111 changes autonomously. Since the carriage 116 has a caster angle β with respect to a plane parallel to the input disk 111 and the output disk 112, the inclination is such that the velocity vector at the contact portion between the power roller 113 and both the disks 111 and 112 is parallel. Stable at the corners. As a result, the position of the power roller is moved and controlled by pressure control using a hydraulic servo, thereby enabling a stepless speed change.

  By the way, in the toroidal type continuously variable transmission of Patent Document 1 described above, for example, three power rollers are arranged between the input disk and the output disk, and a hydraulic servo or a power roller is provided for each of the three power rollers. A link mechanism or the like for connecting the two is necessary, and the configuration becomes complicated.

  Therefore, the position control of the position of the power roller is made possible so that the sun gear disposed on the inner peripheral side of the power roller, the ring gear disposed on the outer peripheral side of the power roller, and the sun gear and the ring gear mesh with each other. And a planet gear combined with a rotating shaft that supports the power roller in a tiltable and rotatable manner, and the sun gear and the ring gear are rotationally driven in the same direction to slide the power roller. There has been proposed a toroidal continuously variable transmission that enables autonomous continuously variable transmission control by changing the inclination angle of the power roller by making the velocity vector of the contact portion different (see Patent Document 2). ).

JP 2006-292079 A International Publication No. WO 05/121602 A1

  By the way, in the toroidal type continuously variable transmission as described above, a traction force (F11) acts when torque is transmitted from a drive source such as an engine to the power roller from the input disk, and the output disk from the power roller. The traction force (F12) also acts when transmitting torque to the power roller, and in order to support the power roller, the reaction force (F13) that balances the traction force (F11 + F12) must be applied. Of course, when performing the shift control, the reaction force is output to the power roller and the driving force for controlling the movement of the power roller is output.

  For this reason, even in the toroidal-type continuously variable transmission of Patent Document 2, it is necessary to continuously apply a reaction force to the power roller via the sun gear and the ring gear, especially during traveling, and a large drive that can withstand the reaction force. It is necessary to provide a hydraulic servo for generating force, a hydraulic circuit thereof, and the like, which has been a factor that hinders the downsizing of the toroidal continuously variable transmission.

  Further, the toroidal continuously variable transmission as described above always cancels the traction force in order to maintain the position of the power roller even in a traveling state at a constant gear ratio without performing the shift control. It was necessary to control the reaction force. That is, the traction force acting on the power roller changes greatly when the driving state is switched according to the driving situation (for example, uphill road, downhill road, etc.) or the ON / OFF of the accelerator by the driver. Since it is difficult to predict a change in traction force, it is necessary to control the reaction force output to the power roller so as to follow these traction forces with good responsiveness.

  Therefore, in the above-described toroidal continuously variable transmission, the control mechanism of the hydraulic servo that rotates the sun gear and the ring gear while outputting the reaction force requires a control mechanism capable of performing complex control such as feedback control, for example. There is a problem that the structure of the toroidal continuously variable transmission is complicated.

  Therefore, an object of the present invention is to provide a continuously variable transmission that can eliminate the need for the rotational driving means to carry a reaction force against the traction force generated in the power roller.

The present invention according to claim 1 (see, for example, FIGS. 1 to 4), a power roller (14) sandwiched between both disks (11, 12) comprising an input disk (11) and an output disk (12),
Sun gears (25A, 25B) disposed on the inner peripheral side between the disks (11, 12);
Ring gears (26A, 26B) disposed on the outer peripheral side between the disks (11, 12);
A rotary tilt support portion (31) that supports the power roller (14) rotatably and tiltably with respect to both the disks (11, 12), and supports the rotary tilt support portion (31) and has one end side thereof. A planetary gear (33) having a support shaft (32) meshing with the sun gear (25A, 25B) and having the other end meshing with the ring gear (26A, 26B), a toroidal continuously variable transmission (2) ), In the continuously variable transmission (1) housed in the case (6),
The toroidal continuously variable transmission (2) is:
Rotational drive means (29) for rotationally driving at least one of the sun gear (25A, 25B) and the ring gear (26A, 26B);
A control pinion that is disposed between the sun gear (25A, 25B) and the ring gear (26A, 26B) and has one end meshed with the sun gear (25A, 25B) and the other end meshed with the ring gear (26A, 26B). (27) and
A carrier (28) that rotatably supports the control pinion (27),
The toroidal continuously variable transmission (2) rotates the sun gear (25A, 25B) and the ring gear (26A, 26B) in the opposite directions via the control pinion (27) by the rotation driving means (29). When the inclination angle of the support shaft (32) of the planet gear (33) is changed by driving, the power roller (with respect to the rotational direction of the disks (11, 12) via the rotary inclination support portion (31) ( The angle of 14) is changed, and due to the difference in the rotation direction of the contact portion (17) with respect to the both disks (11, 12) of the angle-changed power roller, the power roller has a contact radius of the contact portion (17). The posture is autonomously changed so as to return to the tangential direction of the rotational direction of the both disks (11, 12) while tilting in the direction in which the disk is changed. In will make changes of gear ratio,
The carrier (28) is fixed to the case (6).
The continuously variable transmission (1) is characterized by the above.

According to a second aspect of the present invention (see, for example, FIG. 2), the rotation driving means is constituted by a motor (29).
The continuously variable transmission (1) according to claim 1, wherein the continuously variable transmission (1) is provided.

According to a third aspect of the present invention (see, for example, FIGS. 3 and 4), the rotation tilt support portion (31)
It is fixedly supported by the support shaft (32) and is formed in a columnar shape centered on the first axis (I) with a caster angle (γ) given to the axis (H) orthogonal to the support shaft. A central support (35),
The center support portion (35) is rotatably supported with respect to the cylindrical arc surface (36), and is formed in a columnar shape centering on a second axis (J) orthogonal to the first axis (I). A roller rotation support portion (37),
The power roller (14) is supported so as to be rotatable about the second axis (J) with respect to a cylindrical arc surface (38) of the roller rotation support portion (37),
When the planet gear (33) is controlled to rotate and the support shaft (32) is tilted, the rotation / inclination support portion (31) is rotated by the cylindrical parallel surface of the center support portion (35). By supporting the support portion (37) and the power roller (14), the power roller is inclined with respect to the rotation direction of the two disks (11, 12), and the difference in the rotation direction at the contact portion (17). When the power roller is inclined in a direction in which the contact radius of the contact portion (17) is changed by the cylindrical arc surface (36) of the center support portion (35), the first shaft (I) is The power roller is tilted as a center and returned to the tangential direction of the rotational direction of the two disks (11, 12) based on the caster angle (γ).
The continuously variable transmission (1) according to claim 1 or 2, characterized by the above.

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, since the carrier fixed to the case rotatably supports the control pinion that meshes with each of the sun gear and the ring gear, the traction force acts on the power roller. The reaction force is transmitted to the sun gear and the ring gear via the planet gear, and the reaction force of the traction force transmitted to the sun gear and the ring gear is applied to the case via the control pinion and the carrier. A force can be carried, and it is not necessary for the rotational drive means to carry a reaction force against the traction force generated in the power roller. This eliminates the need for a mechanism (hydraulic servo, its hydraulic circuit, etc.) for outputting a large driving force with respect to the traction force. For example, it is possible to configure a rotational driving means by a motor, The continuously variable transmission can be made compact.

  In addition, the reaction force against the traction force generated in the power roller can be carried on the case, so the reaction force against the traction force that changes in a difficult-to-predict situation during driving can be carried on the case, and follows the traction force. Thus, it is not necessary to perform the reaction force output control by the rotation driving means, and a control mechanism for performing complicated control such as feedback control can be eliminated, and the continuously variable transmission can be simplified. And cost reduction.

  According to the second aspect of the present invention, since the rotation driving means is constituted by a motor, the rotation driving means can be simplified as compared with the case where the rotation driving means is constituted by a hydraulic servo, for example. The transmission can be made compact. In particular, when a motor that can control its position in response to an electrical command, such as a stepping motor, is used as the rotational drive means, a device that detects and feeds back the position of the sun gear, ring gear, etc. is not required. Thus, the continuously variable transmission can be simplified and the cost can be reduced.

  According to the third aspect of the present invention, when the planet gear is controlled to rotate and the support shaft is tilted, the rotating and tilting support portion is rotated in the rotation direction of both disks by the cylindrical parallel surface of the center support portion. When the power roller can be inclined with respect to the direction in which the contact radius of the contact portion is changed due to the difference in the rotation direction of the contact portion, the cylindrical shape of the center support portion The arc surface allows the power roller to be tilted and returned to the tangential direction of the rotation direction of both disks based on the caster angle, so that both the rotation centers of the power rollers can be moved by simply controlling the planet gear rotation. It is possible to autonomously change the contact radius of the power roller to the disk and return it to the tangential direction of the rotation direction of both disks. Thereby, since the movement of the power roller in the circumferential direction with respect to both disks can be eliminated, it is possible to fix the carrier that rotatably supports the control pinion to the case (to make it impossible to move).

  Hereinafter, an embodiment of the present invention will be described with reference to FIGS.

  As shown in FIG. 1, a continuously variable transmission 1 according to an embodiment of the present invention includes a toroidal continuously variable transmission (hereinafter simply referred to as a variator) 2, a reversing gear mechanism, a low / high switching mechanism, and the like. A planetary gear device (not shown) made up of is formed inside a mission case (case) 6.

  The variator 2 is a full toroidal continuously variable transmission, and includes two input disks 11 and 11 connected on the input shaft 3, an output disk 12 connected to the output member 16 on the outer peripheral side, and two pieces. A power roller unit 5 (see FIG. 3), which will be described in detail later, having a plurality of power rollers 14 sandwiched between the input disks 11 and 11 and one output disk 12 is provided. The input disks 11 and 11 and the output disk 12 have arc-shaped concave grooves forming a part of a circle so as to face each other, and form double cavities 13 and 13 with two rows of power rollers interposed therebetween. Thus, it is configured to cancel the thrust force between the input disks.

  A plurality of power rollers 14 (for example, three in one cavity) are arranged at substantially equal positions in the circumferential direction in the annular double cavities 13, 13, and the rotation axis of the power roller 14 is controlled by the roller control device 4. Can be tilted and the power roller 14 is rotationally controlled. Further, the input discs 11 and 11 are pressed in a closed loop by the hydraulic servo 8 to sandwich the power roller 14, and the clamping pressure is controlled by the hydraulic pressure. The power roller 14 tilts autonomously by the rotation control by the roller control device 4 and the clamping pressure of the input disks 11 and 11, thereby changing the contact radius between the input disks 11 and 11 and the output disk 12. And continuously shifting continuously. In the variator 2, since the output disk 12 is inverted with respect to the input disks 11 and 11, the speed ratio is-(minus).

  The roller control device 4 includes sun gears 25A and 25B disposed on the inner peripheral side of the power roller 14 and rotatably supported by the input shaft 3, and being rotationally connected to each other by a sleeve member 25a, The ring gears 26A and 26B, which are arranged on the outer peripheral side of the power roller 14 and are rotatably supported with respect to the input shaft 3, and the sun gears 25A and 25B and the ring gears 26A and 26B are arranged to mesh with each other. A motor unit 29 (FIG. 2) as a rotational drive means for rotationally driving the carrier 28 fixed to the transmission case 6, the power roller unit 5, and the ring gear 26A. See).

  The carrier 28 includes a front main carrier plate 28a, a front sub carrier plate 28b, a rear sub carrier plate 28c, and a rear main carrier plate 28d. The front main carrier plate 28 a is formed with a sleeve portion 28 g on the inner peripheral side, and the sleeve portion 28 g is rotatably supported by the input shaft 3 via a bearing 43. The front main carrier plate 28 a has a connection portion 28 s formed on the outer peripheral side, and the connection portion 28 s is fixed to the inner surface of the transmission case 6. Further, a pinion shaft 28e is integrally formed on the front main carrier plate 28a, and a control pinion 27 (to be described later) is rotatably supported via bearings 41 and 41.

  The front sub-carrier plate 28b has a hole 28h that fits into a projection 28f formed on the pinion shaft 28e, and is fixed to the front main carrier plate 28a in the hole 28h. Further, the front sub-carrier plate 28b is formed with a sleeve portion 28i on the inner peripheral side, and is disposed on the outer peripheral side of the sleeve member 25a.

  The rear main carrier plate 28 d has a sleeve portion 28 m on the inner peripheral side, and the sleeve portion 28 m is rotatably supported by the input shaft 3 via a bearing 44. Further, a pinion shaft 28j is integrally formed on the rear main carrier plate 28d, and the control pinion 27 is rotatably supported via bearings 42 and 42.

  The rear sub-carrier plate 28c is formed with a hole 28l that fits into a protrusion 28k formed on the pinion shaft 28j, and is fixed to the rear main carrier plate 28d in the hole 28l. The rear sub-carrier plate 28c has a sleeve portion 28n formed on the inner peripheral side, and is disposed on the outer peripheral side of the sleeve member 25a. The front sub-carrier plate 28b and the rear sub-carrier plate 28c are connected to each other on the inner peripheral side of the output disk 12, whereby the front main carrier plate 28a, the front sub-carrier plate 28b, and the rear sub-carrier plate 28c. The carrier 28 constituted by the rear main carrier plate 28d is fixed to the transmission case 6. The output disk 12 is rotatably supported via bearings 45 and 45 at the portion where the front subcarrier plate 28b and the rear subcarrier plate 28c are connected.

  The control pinion 27 on the left side in FIG. 1 among the control pinions 27 and 27 is disposed between the adjacent power rollers 14 in the cavity 13 and meshes with each other between the sun gear 25A and the ring gear 26A. A pinion shaft 28e formed integrally with the carrier 28 is rotatably supported via bearings 41 and 41. Similarly, the control pinion 27 on the right side in FIG. 1 is also disposed between the adjacent power rollers 14 in the cavity 13, and meshes with the sun gear 25B and the ring gear 26B, and is integrated with the carrier 28. The pinion shaft 28j is formed in a rotatable manner via bearings 42, 42.

  As described above, for example, six power roller units 5 are arranged in two cavities, and all the six power roller units 5 have the same configuration. As shown in FIG. 3, the power roller unit 5 is formed in a shape in which the movable range of the power roller 14 is cut out from an annular gear, and the inner peripheral side (for example, the lower side in the figure) is a sun gear 25A (25B). And a planet gear 33 whose outer peripheral side (for example, the upper side in the figure) meshes with the ring gear 26A (26B), and is fixedly supported by the center portion of the planet gear 33, and the power roller 14 is rotatable in the ω1 direction. It is comprised by the rotation inclination support part 31 supported so that it can incline in omega2 direction freely.

  The rotation tilt support portion 31 is composed of a center support portion 35 and a roller rotation support portion 37. The center support portion 35 is integrally formed (fixed support) with the support shaft 32, and is caster in a plane orthogonal to the support shaft 32 from an axis H that is orthogonal to the support shaft 32 and parallel to both the disks 11 and 12. It is formed in a cylindrical shape centering on an axis (first axis) I inclined by an angle γ. The roller rotation support portion 37 is rotatably supported with respect to the cylindrical arc surface 36 of the center support portion 35, and an axis (second axis) J that is orthogonal to the axis I and serves as the rotation axis of the power roller 14. It is formed in a cylindrical shape with a center. Further, the roller rotation support portion 35 rotatably supports the power roller 14 that rotates about the axis J by a cylindrical arc surface 38.

  As shown in FIG. 2, the motor unit 29 is disposed on the lower side of the variator 2 inside the mission case 6, and has a drive unit 29a and a rack unit 29b made of a stepping motor. The drive unit 29a is provided with a rotor unit (not shown) that is rotated in accordance with the traveling state of the vehicle based on a signal from an electronic control unit (not shown). The rack portion 29b is connected via a screw mechanism (not shown) that converts to linear motion. The rack portion 29b is a rack-like member having a plurality of teeth 29c formed on the upper surface side, and the teeth 29c mesh with external teeth 26a formed on the outer peripheral surface of the ring gear 26A.

  Next, the operation of the variator 2 will be described with reference to FIG.

  In the variator 2 mounted on the vehicle, the rotation of the input shaft 3 connected to the engine output shaft is transmitted to the input disks 11 and 11 of the variator 2. The power roller 14 rotates based on the rotation of the input disks 11 and 11, and the output disk 12 is rotated in the ω3 direction based on the rotation as shown in FIG. Then, in the cavity 13, a traction force F1 generated when torque is transmitted from the input disk 11 to the output disk 12 acts on the power roller 14, and this traction force F1 is a reaction force F2 received by the ring gear 26A and the sun gear 25A. It matches with ', F3'.

  From this state, as shown in FIG. 4B, for example, when the ring gear 26A is rotationally driven in the ω4 direction by the motor unit 29, the planet gear 33 of the power roller unit 5 rotates in the same direction as the ring gear 26A. As shown in FIG. 2, the control pinion 27 rotates about the pinion shaft 28e of the carrier 28, and the meshed sun gear 25A rotates in the ω5 direction opposite to the ring gear 26A (see FIG. 4B). Let For this reason, as shown in FIG. 4B, the power roller unit 5 is rotated in the ω4 direction from the ring gear 26A and is rotated in the ω5 direction from the sun gear 25A, and is rotated (autorotated) at the original position. 32 will change the angle. At this time, the power roller 14 is inclined toward the rotation direction ω <b> 3 of the output disk 12 together with the roller rotation support portion 37 by a cylindrical parallel surface provided in the center support portion 35 of the rotation inclination support portion 31.

  Then, at the contact portion 17 between the output disk 12 and the power roller 14, the speed vector Vr of the power roller 14 is directed to the inner peripheral side with respect to the tangential direction of the output disk 12, and the speed vector Vd of the output disk 12 is Therefore, the velocity vector Vd of the output disk 12 and the velocity vector Vr of the power roller 14 are not parallel to each other. Further, in the contact portion 17, a traction force F4 in the same direction as the direction of the difference between the velocity vector Vd and the velocity vector Vr is generated, and the traction force F4 acts on the power roller 14.

  On the other hand, a similar action occurs between the power roller 14 and the input disk 11, and a traction force opposite to the traction force F4 acts on the power roller 14. Due to the action of the traction force and the traction force F4 generated between the power roller 14 and the input disk 11, as shown in FIG. 4C, the rotation axis J (see FIG. 3) of the power roller 14 is the axis I And the velocity vector Vr of the power roller 14 and the velocity vector Vd of the output disk 12 by the action of the caster angle γ (see FIG. 2) while being tilted along the arc surface 36 provided in the center support portion 35. Are in parallel positions. That is, the gear ratio (contact radius) of the output disk 12 with respect to the input disk 11 changes autonomously.

  Next, the balance of force of the variator 2 will be described. Even when the variator 2 is in a traveling state at a constant gear ratio where no speed change control is performed, when the torque is transmitted between the input disk 11 and the output disk 12, the traction force F1 is applied to the power roller 14. Occurs. As shown in FIG. 2, the traction force F1 is decomposed into a force F2 acting on the outer peripheral side end of the variator 2 in the planet gear 33 and a force F3 acting on the inner peripheral side end of the variator 2 in the planet gear 33. Is done.

  The force F2 is transmitted to the ring gear 26A as a force F5 that attempts to rotate the ring gear 26A in the clockwise direction in the drawing because the planet gear 33 and the ring gear 26A are engaged with each other. The force F5 transmitted to the ring gear 26A is transmitted to the control pinion 27 as a force F7 that attempts to rotate the control pinion 27 in the clockwise direction in the drawing by engaging the ring gear 26A and the control pinion 27. Is done.

  On the other hand, the force F3 is transmitted to the sun gear 25A as a force F6 for rotating the sun gear 25A in the clockwise direction in the drawing because the planet gear 33 and the sun gear 25A are engaged with each other. The force F6 transmitted to the sun gear 25A is applied to the control pinion 27 as a force F8 that attempts to rotate the control pinion 27 counterclockwise in the figure because the sun gear 25A and the control pinion 27 are engaged with each other. Communicated.

  The forces F7 and F8 act on the pinion shaft 28e that rotates the control pinion 27 in the opposite direction, that is, on the pinion shaft 28e that rotatably supports the control pinion 27. The force F9 is an attempt to move in the clockwise direction, and this force F9 acts on the transmission case 6 (see FIG. 1) via the carrier 28.

  Further, since the force F9 is a force obtained by combining F7 and F8 having the same magnitude as the forces F2 and F3 decomposed from the traction force F1 as described above, the force F9 has the same magnitude as the traction force F1. The force F1 and the force F9 are the planet gear 33 and the control pinion 27 because the rotation center of the planet gear 33 (power roller 14) and the pinion shaft 28e are substantially on the same diameter with respect to the input disk 11. It is possible to obtain a suspended state without rotating. That is, the traction force F1 generated in the power roller 14 is all acting on the mission case 6, and all the reaction force against the traction force F1 can be carried on the mission case 6.

  Although the reaction forces of these traction forces F1 to F9 are omitted in FIG. 2, they can be shown as reaction forces F1 ′ to F9 ′, and arrows in directions opposite to the respective arrows. That is, as shown in FIG. 4A, reaction forces F2 ′ and F3 ′ are shown as explanations of the force acting on the power roller unit 5.

  Further, when the variator 2 performs shift control, the ring gear 26 </ b> A is rotationally driven by the motor unit 29 as described above while transmitting torque between the input disk 11 and the output disk 12. That is, the ring gear 26A is rotationally driven by the motor unit 29, and the planet gear 33 and the control pinion 27 rotate (spin). However, the planet gear 33 and the control pinion 27, and the ring gear 26A and the sun gear 25A are engaged with each other. There is no change, and there is no change in the force relationship that causes the reaction case 6 to carry the reaction force of the traction force F1 generated in the power roller 14 as described above. Therefore, the motor unit 29 can drive the ring gear 26A with a driving force that does not carry these reaction forces. That is, the motor unit 29 can dispense with a mechanism such as a hydraulic servo or a hydraulic circuit for outputting a large driving force with respect to the traction force F1.

  In the continuously variable transmission 1 according to the present invention, the control pinion 27 is disposed between the power rollers 14. However, as described above, the power roller unit 5 that supports the power roller 14 performs the shift control. At this time, the power roller 14 rotates (spins) on the spot and the power roller 14 does not move in the rotational direction with respect to both the disks 11, 12.

  In the above description, one power roller 14 in the cavity 13 has been described as an example. However, these actions simultaneously act on the three power rollers 14 in one cavity 13, and another cavity 13. Similarly, the shift operation is performed by acting on the three power rollers 14. The continuously variable speed rotation is output from the output member 16 connected to the output disk 12 and input to the above-described planetary gear device (not shown) as shown in FIG.

  In the continuously variable transmission 1 described above, the carrier 28 fixed to the transmission case 6 rotatably supports the control pinions 27 and 27 that mesh with the sun gears 25A and 25B and the ring gears 26A and 26B, respectively. Therefore, even when the traction force F1 is applied to the power roller 14, the reaction force is transmitted to the sun gears 25A and 25B and the ring gears 26A and 26B via the planet gear 33, and the sun gears 25A and 25B and the ring gears 26A and 26B are transmitted. By applying the reaction force of the transmitted traction force F1 to the transmission case 6 via the control pinions 27 and 27 and the carrier 28, the transmission force of the traction force F1 can be carried on the transmission case 6, and the motor unit. 29 is a torque generated in the power roller 14 That carries the reactive force against the emission force F1 can be omitted. Thereby, a mechanism (hydraulic servo, its hydraulic circuit, etc.) for outputting a large driving force with respect to the traction force F1 can be eliminated, and the continuously variable transmission 1 can be made compact.

  Further, since it becomes possible to carry the reaction force against the traction force F1 generated in the power roller 14 on the mission case 6, the reaction case against the traction force F1 that changes in a difficult-to-predict situation during traveling is also carried on the mission case 6. Therefore, it is not necessary to perform reaction force output control by the motor unit 29 so as to follow the traction force F1, and a control mechanism for performing complicated control such as feedback control can be eliminated. In addition, the continuously variable transmission 1 can be simplified and the cost can be reduced.

  In addition, since the rotation driving means is constituted by a motor, the rotation driving means can be simplified as compared with the case where the rotation driving means is constituted by a hydraulic servo, for example, and the continuously variable transmission 1 can be made compact. be able to. In particular, when a stepping motor, that is, a motor capable of controlling its own position in response to an electrical command is used as the motor unit 29, a device that detects and feeds back the positions of the sun gears 25A and 25B, the ring gears 26A and 26B, and the like. The continuously variable transmission 1 can be simplified and the cost can be reduced.

  Further, when the planet gear 33 is controlled to rotate and the support shaft 32 is inclined, the rotation / inclination support portion 31 is rotated with respect to the rotation direction of the disks 11 and 12 by the cylindrical parallel surface of the center support portion 35. When the power roller 14 is tilted in a direction in which the contact radius of the contact portion 17 is changed due to a difference in the rotation direction of the contact portion 17, the center support portion 35 is then tilted. The cylindrical circular arc surface 36 allows the power roller 14 to be tilted and returned to the tangential direction of the rotation directions of both the disks 11 and 12 based on the caster angle γ. Without moving the rotation center of the roller 14, the contact radius of the power roller 14 with respect to both the disks 11, 12 is changed, and both the disks 11, 1 are changed. It can be performed to return to the tangential direction of the rotation direction of the autonomously. As a result, the circumferential movement of the power roller 14 with respect to both the disks 11 and 12 can be eliminated, so that the carrier 28 that rotatably supports the control pinion 27 is fixed to the transmission case 6 (not movable). Can be made possible.

  In the continuously variable transmission 1 according to the present embodiment, the ring gear is described as being rotationally driven by the rotational driving means, but the sun gear or the sun gear and the ring gear are rotationally driven by the rotational driving means. Even the present invention can be applied.

  Further, in the continuously variable transmission 1 according to the present embodiment, the rotation driving means has been described as the motor unit 29 configured by the stepping motor and the screw mechanism. The rotation driving means may be configured, that is, the present invention can be applied to any mechanism that can rotate and drive at least one of the sun gear and the ring gear.

The partial cross-sectional view which shows the continuously variable transmission which concerns on this invention. The fragmentary longitudinal cross-section which shows a toroidal type continuously variable transmission. The perspective view which shows a power roller unit. FIG. 4 is a schematic diagram showing a part of a toroidal continuously variable transmission, where (a) shows a state where force is applied, (b) shows a state where the power roller unit is rotated, and (c) shows that the power roller is inclined. The state of the state. It is the schematic diagram of the state with the force balance which shows the conventional toroidal type continuously variable transmission, (a) is a radial view, (b) is an axial view. It is a schematic diagram of the state which moved the power roller which shows the conventional toroidal type continuously variable transmission, (a) is radial direction view, (b) is axial direction view. The power roller which shows the conventional toroidal type continuously variable transmission is a schematic diagram of the state which inclined, (a) is radial direction view, (b) is an axial view.

Explanation of symbols

1 continuously variable transmission 2 toroidal continuously variable transmission 6 case (mission case)
DESCRIPTION OF SYMBOLS 11 Input disk 12 Output disk 14 Power roller 17 Contact part 25A, 25B Sun gear 26A, 26B Ring gear 27 Control pinion 28 Carrier 29 Rotation drive means, motor (motor unit)
31 Rotating and tilting support portion 32 Support shaft 33 Planet gear 35 Center support portion 36 Arc surface 37 Roller rotation support portion 38 Arc surface H Axis (axis)
I 1st axis (axis)
J Second axis (axis)

Claims (3)

A power roller sandwiched between both an input disk and an output disk;
A sun gear disposed on the inner peripheral side between the two disks;
A ring gear disposed on the outer peripheral side between the two disks;
A rotation / inclination support portion that supports the power roller in a rotatable manner and in an inclined manner with respect to the two disks, and supports the rotation / inclination support portion, with one end meshing with the sun gear and the other end meshing with the ring gear. In a continuously variable transmission in which a toroidal-type continuously variable transmission including a planetary gear having a support shaft is housed in a case,
The toroidal continuously variable transmission is
Rotation driving means for rotating at least one of the sun gear and the ring gear;
A control pinion disposed between the sun gear and the ring gear, one end side meshing with the sun gear and the other end side meshing with the ring gear;
A carrier that rotatably supports the control pinion,
The toroidal continuously variable transmission changes the rotation angle of the planet gear support shaft by rotating the sun gear and the ring gear in opposite directions through the control pinion by the rotation driving means. The angle of the power roller with respect to the rotation direction of the two disks is changed via the inclined support part, and the power roller is changed to the contact part by the difference in the rotation direction in the contact part with respect to the two disks of the angle-changed power roller. The gear ratio is changed by autonomously changing the posture so as to return to the tangential direction of the rotational direction of the two disks while tilting in the direction in which the contact radius is changed,
The carrier is fixed to the case.
A continuously variable transmission. The rotation driving means is constituted by a motor.
The continuously variable transmission according to claim 1. The rotation tilt support part is
A center support portion formed in a columnar shape around a first axis that is fixedly supported by the support shaft and has a caster angle with respect to an axis orthogonal to the support shaft;
A roller rotation support portion that is rotatably supported with respect to the cylindrical arc surface of the center support portion and is formed in a column shape centering on a second axis orthogonal to the first axis,
The power roller is supported so as to be rotatable about the second axis with respect to a cylindrical arc surface of the roller rotation support portion,
The rotation tilt support portion supports the roller rotation support portion and the power roller by a cylindrical parallel surface of the center support portion when the planet gear is rotationally controlled and the support shaft is tilted. When the power roller is inclined with respect to the rotation direction of the two disks, and the power roller is inclined in a direction in which the contact radius of the contact portion is changed due to a difference in the rotation direction of the contact portion, A cylindrical arcuate surface is made to return to the tangential direction of the rotational direction of the two disks based on the caster angle while tilting the power roller about the first axis.
The continuously variable transmission according to claim 1 or 2.

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